Variable-speed-transmission gearing.



A. 11. 000KB,

VARIABLE SPEED TRANSMISSION GEARING.

APPLICATION FILED MA! 11, 1912.

Patented Nov. 4, 1913.

3 SHEETS-SHEET l.

iwe nfoz A. H. 000KB.

VARIABLE SPEED TRANSMISSION GBARING.

APPLICATION FILED MAY 11, 1912.

1 ,O7 7,4;54,, I Patented Nov. 4, 1913.

a SHEETSSHEET 2.

Y 6.0 I A G h 0 0 e I I O If I A. H. 000KB.

VARIABLE SPEED TRANSMISSION GEARING.

APPLICATION FILED MAY 11, 1912.

Patented Nov. 4, 1913.

3 BHEETB SHEET 3.

/ 7 f 7 1 III- shaft J are obtained by relative adjustments of the crank pins f of the fluid pressure device. Thus, under those conditions in which the driven shaft G is brought to a state of rest, the influence exerted by the main gearing alone on the driven shaft to communicate motion thereto is exactly counteracted .by an equal and opposite influence exerted by the fluid pressure variable 'speed transmission. By still further increasing the opposing influence of the fluid pressure transmission to such an extent that its influence is greater than the influence of the main gearing alone on the driven shaft G, a re- ,versal of motion of the driven shaft G with reference to the direction of rotation under normal speed will result. Furthermore, the speed of the driven shaft between the limits of a speed in excess of the normal speed of the driven shaft down to an actual reversal of speed of the driven shaft may be enhanced or diminished by infinitely small amounts.

At some definite predetermined ratio between the speeds of the driving and driven shafts as described, the power or motion will be transmitted entirely through the main gearing, which may be as shown a train of gears or differential earing, and no power will be transmitted t rough the fluid pressure controlling device, and the speed of the driven shaft. at this predetermined ratio I have termed the normal speed of the driven shaft.

The work of the relatively less eflicient fluid pressure device is minimized as compared with the work it would perform if operating alone as a variable speed gearing, and the work of the more eflicient main gearing relative to the fluid pressure device is maximized, so that the function of the fluid pressure device is to increase or decrease the speed of the driven shaft above or below normal speed, at which normal speed no power will be transmitted by the fluid pressure device, and all the power will be transmitted by the main gearing.

In minimizing the work performed by the fluid pressure device, I am able to reduce its dimensions for a given amount of power to be delivered to the driven shaft, reduce the wear and tear of moving parts, reduce frictional losses, reduce losses due to heating of the fluid used in the fluid pressure device, and maintain a higher degree of efliciency for a longer period after deterioration of the fluid pressure device has set in.

Since the efficiency of power transmission by gearing is greater than by fluid pressure,

the efficiency of my improved apparatus will equal the higher efficiency of the main gearing at the normal speed of the driven shaft; and within reasonable limits above and below the normal speed of the driven shaft the efficiency of my apparatus will artake more largely of the relatively high e V ciency of the main gear train, than of the relatively low efliciency of the fluid pressure controlling devices. For instance, if the assumed efficiency of the main gear train alone is 95% and that of the fluid pressure'device alone is 60%, then at infinitely small speeds of the driven shaft in either direction-and also at a speed of 100% in excess of the normal speed of the driven shaft, the efficiency of my apparatus partakes equally of the eiflciencies of the main gearing and fluid pressure device, which under these circumstances would transmit equal amounts of power, and the efficiency of theapparatus would be equal to the average efliciency for the two or 73%. At the normal speed of the driven shaft, however, the efficiency of the apparatus would be 95% or equal to that of the main gearing. At intermediate points between these limits the efliciency of my apparatus will range from 775% to 95%, as contrasted with the assumed cfliciency of 60% of the fluid pressure device when operating alone and without the main gearing, and at such intermediate points the efliciency of my apparatus will partake of the individual efficiencies of the main gearing and the fluid pressure device in direct proportion to the power transmitted by each. For instance, when the driven shaft is operated at a speed of 50% of the normal speed or at 50% in excess of the normal speed,then

clearness and brevity. In this form of the apparatus, the main differential gearing is interposed between the main driving shaft 2 and the driven shaft 3. The bevel gear H is fast to the driving shaft '2, andthe bevel gear J forms a part of or is otherwise secured fast to a sleeve 4 loose on the driven shaft 3. The bridle L carrying "the bevel pinions K is fast to the driven shaft 3 as before. The shaft 2 and sleeve'4 are 'jour-1 naled in bearings 5 and 6 in the casing K which surrounds the main differential gearing and the pump structure and motor struchave shown a fluid and the ports 8 at one side are connected by the pipe or passage 10 while those at the other side are connected by the piping 11, so that the motive fluid passes through the ports at one side of the center and through pipe 10 from the pump to the motor, and returns through the ports at the other s1de and through connection 11 from the motor to the pump.

Since the pump and motor sections of the device are similar, but one will be described,

omitting details of construction which are not essential to an understanding of the principles of operation. The pump cylinder barrel 13 is connected to rotate with the driving shaft 2 while the motor cylinder barreel 14 is connected to rotate the sleeve 4. The pump cylinders 15 are provided with ports 16 adapted to register with the ports in the mid plate 8 and the cylinders 15 are provided with reciprocating pistons 17 suitably connected by piston rods 18 to a socket ring 19 having trunnions 24 pivoted to a universal joint ring 20 pivoted at 21 at each side to the driving shaft 2. The socket ring 19 turns on a track or guide formed by balls 22 which run in a ring or box 23 pivoted to the sides of the casing 7 in such manner (shown in Fig. 7 that the axes of the trunnions 24, pivots 21, and the pivots of the box 23 will intersect at the same point. The ring or box 23 is provided with a toothed segment 25 having operative connections by means of which the ring may be rotated through the agency of a' shaft 26 to which a hand wheel 27 may be connected, for varying the angle of the-box 23 and connected parts. In this manner, the throw of the pistons 17 is varied and the speed and direction of rotation of the motor barrel 14 is varied, thereby controllin the speed and direction of rotation of the s eeve 4 and gear J of the differential gearing.

In the operation of the apparatus shown in Fig. 5, power is applied to the driving shaft 2 through the ear or pulley F and the ring 19 is rotate thus actuating the pistons '17 In the cylinder barrel 13 to circulate the motor fluid'between the pump and motor through the valve ports and connections 10 and 11. The gear H is rotated with the driving shaft, and the gear J is rotated with the pump barrel 14, in either direction and at varying speeds, or else the gear J is held stationary, according to the adjustment of the box 23 of the pump, and the operation of the differential gearing is thus controlled in the same manner as described in conneotion with Fig. 1, the principles of operation being the same.

I am not to be understood as limiting the invention to the constructions shown, as different combinations'of elements may be devised without departing from the spirit of the invention.

I claim and desire to obtain by Letters Patent the following:

1. In variable speed transmission gearing, the combination of the driving and driven shafts, positively acting variable transmission devices connecting said shafts, and positively acting fluid pressure means operatively connected with the driving shaft for controlling said transmission devices, and thereby positively varying the speed and direction of rotation of the driven shaft by infinitely small amounts between predetermined llmits.

2. In variable speed transmission gearing, the combination of the driving and driven shafts, positively actingv variable transmission devlces connecting said shafts, and positively acting fluid pressure controlling means operatively connected with the driving shaft and connected to one member of the variable transmission devices, for controlling said devices and thereby positively varying the speed and direction of rotation of the driven shaft by infinitely small amountsbetween predetermined limits.

3. In variable speed transmission gearing, the combination of the driving and driven shafts, positivelyacting variable transmission devices connectin said'shafts and having a movable controlling member, and ositively acting fluid pressure contro ling means operatively connected with the driving shaft and connected to said movable controlling member for positively varying the speed and direction of rotation of the driven shaft by infinitely small amounts between predetermined limits.

4. In variable speed transmission gearing, the combination of the driving and driven shafts, positively acting variable transmission devices connectin said shafts and having a movable controlllng member, and positively acting controlling apparatus for the transmission devices comprlsing a fluid pressure pump operatively connected with the driving shaft and a fluid pressure motor driven by the pump and connected to the said movable controlling member, for posi tively varying the speed and direction of rotation of the driven shaft by infinitely small amounts between predetermined limits.

5. In variable speed transmission gearing, the combination of the driving and driven shafts, positively acting differential gearing connecting said shafts having a movable controlling member, and positively acting fluid pressure controlling apparatus comprising a circulating chamber, a pump operatively connected with the driving shaft and a motor connected to the said movable controlling member, whereby the speed and direction of rotation of the driven shaft are positively varied by infinitely small amounts between predetermined limits.

6. In variable speed transmission gearing, the combination of the driving and driven elements, positively acting variable transmission devices connecting said elements and having a movable controlling member, and positively acting controllin apparatus for actuating said movable mem er and for controlling the speed and direction of rotation of said movable member, comprising a fluid pressure pump operatively connected with the driving element and adapted to be continuously actuated in one direction, and a fluid pressure motor connected to said movable member and capable of being driven in either direction at var ing speeds by the continuous operation of t e pum in one direction, whereby the speed and direction of rotation of the driven element are positively varied by infinitely small amounts between predetermined limits.

7. In variable speed transmission gearing, the combination of the driving and driven elements, continuously positive variable transmission devices connecting said elements and havin a movable controlling member, and geontmuously positive controlling apparatus for said variable transmission devices, connected to be actuated continuously in one direction by the driving element and capable of actuating the said movable controlling member in different directions at varying speeds, and connections between said controlling apparatus and said movable member, whereby the speed and direction of rotation of the driven element are positively varied by infinitely small amounts between predetermined limits.

In testlmony whereof I have signed this specification in the presence of two subscribing witnesses.

ALEXANDER H. COOKE. Witnesses:

JOHN ELIAS JONES, Lonn'rra LUCK. 

